Regenerative ranking cycle power plant

ABSTRACT

This invention relates to the regenerative pre-heating of feed liquids by expanded heating vapor discharged from heat engines of vapor power plants within velocity-accelerated contact heat exchangers. The regenerative Rankine cycle invention may operate with any suitable working fluid such as steam or organic vapors, and has potential application to both stationary and vehicular power plant systems.

United States Patent Hull Aug. 29, 1972 [54] REGENERATIVE RANKING CYCLE [56] References Cited L T POWER P AN UNITED STATES PATENTS 2 I ento: Francis H 5 7 2 St 2,268,356 12/1941 Turner ..60/92X 1 r Brooklyn 'f 2,278,085 3/1942 Ostermann ..60/94 p 3,292,372 12/1966 Michael ..60/ 107 X 3,314,236 4/1967 Zanoni ..60/67 1 Filed! 1971 3,336,013 8/1967 Salo ..60/94R pp No 121 795 FOREIGN PATENTS OR APPLICATIONS 108,214 12/1927 Austria ..60/94 RehMUs AP mm 592,994 2/1934 Germany ..60/67 [63] 'Continuation-in-part of Ser. Nos; 889,262, Dec. 'f f' n Schwadmn I 30, 1969, Continuation-impart of Ser. No. f F' 752,120, July 22, 1968, abandoned, Continua- Ammey oben tion-in-part of Ser. No. 690,040, Nov. 14, 1967, abandoned, Continuation-impart of [57] ABSTRACT Ser. No. 621,381, Jan. 23, 1967, abandoned, This invention relates to the regenerative pre-heating Continuation-impart of Ser. No. 403,244, of feed liquids by expanded heating vapor discharged Oct. l 2, l964, abandoned. I from heat engines of vapor power plants within velocity-accelerated contact heat exchangers. The 52 US. Cl. ..60/94, 60/67, 6%?675, regenerative Rankine cycle invention may operate with any suitable working fluid such as steam or orgs/ 7 3 5 9 ganic vapors, and has potential application to both sta- Regener ative 1 Feed Heaters tionary and vehicular power plant systems.

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ATTORNEY REGENERATIVE RANKING CYCLE POWER PLANT The present invention is a continuation-in-part of my presently pending application Ser. No. 889,262 entitled Regenerative Steam Power Plant" and filed Dec. 30, 1969; of my prior patent application Ser. No. 752,120 entitled Regenerative Steam Power Plant and filed July 22, 1968 (now abandoned); of my prior patent application Ser. No. 690,040 entitled Regenerative Steam Power Plant and filed Nov. 14, l967(now abandoned); of my prior patent application Ser. No. 621,381 entitled Regenerative Steam Power Plant and filed Jan. 23, 1967 (now abandoned); and of my prior patent application Ser. No. 403,244 entitled Regenerative Steam Power Plant Process and filed Oct. 12, 1964 (now abandoned).

As used hereinafter, the term fluid shall refer to any liquid or gaseous medium; the term compressible fluid shall refer toany gaseous medium or vapor; the term extracted steam shall relate to low-pressure steam which has been partially and substantially expanded in a particular steam power turbine; the term exhaust steam shall relate to low-pressure steam which has been substantially expanded in a particular steam power turbine or other process apparatus; the term regenerative feed heating shall refer to steam power, plant processes wherein the liquid feed water is pre-heated through heat exchange with extracted steam that has been partially expanded in the power turbine before the liquid feed water is evaporated in the companion steam generator; the term heat engine shall relate to a thermodynamic engine which may convert thermal or molecular energy in the working fluid stream to mechanical energy, or convert mechanical energy to thermal. or molecular energy in the working fluid stream;

the term contact interchange shall refer to the fluidto-fluid exchange of thermal and kinetic energy between adjacent fluid streams having different velocities in parallel flow, and having no physical or mechanical separation between them; the term mixing length shall relate to the effective linear dimension perpendicular to the direction of mean fluid flow within which contact interchange shall take place between a heating fluid stream and a cooling fluid stream; and

the term characteristic length shall relate to the effective linear dimension parallel to the direction of mean fluid flow within which contact interchange shall take place between a heating fluid stream and a cooling fluid stream.

While the apparatus of the invention is described in connection with regenerative feed heating of closedcycle steam power plants,it will be understood by those skilled in the art that variations of the steam power plant processes described using velocity-accelerated contact heat exchange methods may be employed for the purpose of improving and simplifying steam plant processes in other applications.

The primary object of the invention is to provide a simplified steam power plant process employing velocity-accelerated contact interchange methods for the regenerative heating of boiler feed water.

Another important object is to provide a practicable regenerative feed heating means which may pre-heat boiler feed water effectively to near-limiting saturation enthalpies at the pressure of the boiler.

A further object is to provide a compact and practicable regenerative feed heating means which will eliminate the need of utilizing closed surface-type regenerative feed water heaters in connection with steam power plant processes.

An additional object is to provide a compact and practicable regenerative feed heating means for steam power plant processes which will eliminate the need to provide closed surface-type feed water pre-heaters or economizers in the upper works of the steam generator or boiler.

With the foregoing objects in view, together with others which will appear as the description proceeds, the invention resides in the novel assemblage and ar rangement of system components in steam power plant processes which will be described more fully in the discussion, illustrated in the drawings, and particularly pointed out in the claims.

In the drawings:

FIG. 1 is a schematic process diagram of a simplified closed-cycle regenerative Rankine steam power plant wherein a plurality of velocity-accelerated contact heat exchangers are supplied with motive feed water and low-pressure extracted heating steam at common supply pressures, while the plurality of heat exchangers discharge pre-heated boiler feed water to the common boiler supply pressure. The simplified. steam power plant schematic process diagram of FIG. 1 includes a forced-circulation type of steam generator, steam power turbine, steam condenser, deaerating food water heater, liquid feed pumps, and contact-type regenerative feed water heaters.

FIG. 2 is a fragmentary longitudinal sectional view through one of the contact-type regenerative feed waters shown in FIG. 1, the same being in the form of conventional'ejector-type apparatus.

FIG. 3 is a fragmentary view of the schematic diagram of FIG. 1 wherein an alternate type of regenerative feed heater has been substituted for that shown in FIGS. 1 and 2.

FIG. 4 is a fragmentary longitudinal sectional viewthrough the contact-type of regenerative feed heater shown schematically in FIG. 3, the same being of a fonn which is the inverse of the apparatus of FIG. 2.

FIG. 5 is a partial view of FIG. 4 wherein the coniforrn flow divider thereof has been removed from the apparatus of FIG. 4 for purposes of presentation.

FIG. 6 is a transverse sectional view taken along the line 2-2 of FIG. 4.

FIG. 7 is a transverse sectional view taken along the line 3-3 of FIG. 4.

FIG. 8 is a fragmentary schematic process diagram of a closed-cycle regenerative Rankine steam power plant wherein a plurality of velocity-accelerated contact-type feed heaters are supplied with motive feed water at a common supply pressure and individual feed heaters receive extracted turbine heating steam at different pressures while all the feed heaters discharge boiler feed water to the common boiler supply pressure.

FIG. 9 is a fragmentary schematic process diagram of a simplified closed-cycle regenerative Rankine steam power plant wherein a plurality of velocity-accelerated contact heat exchangers are supplied with motive feed water at a common supply pressure and discharge preheated boiler feed water to the common boiler supply pressure, while each contact heat exchanger receives low-pressure extracted heating steam from a separate steam turbine which is supplied from the common steam generator or boiler member.

FIG. 10 is a fragmentary schematic process diagram of a simplified closed-cycle regenerative Rankine steam power plant wherein boiler feed water is heated by extracted steam to a limiting enthalpy corresponding to an intermediate cycle pressure in one velocityaccelerated contact heat exchanger which discharges to a series-connected motive pump and velocity-accelerated contact heat exchanger where the boiler feed water is heated by extracted steam to a higher limiting enthalpy which corresponds to a higher cycle pressure.

FIG. 11 is a fragmentary schematic process diagram of a combinative closed-cycle regenerative steam power plant system wherein a single steam generator serves as the common energy source for separate contact-type regenerative Rankine cycle branches connected in parallel with respect to each other and their common steam generator member.

FIG. 12 is a schematic process diagram of a combinative closed-cycle regenerative steam power plant system wherein a plurality of steam generators are connected in parallel with respect to each other and a 'common contact-type regenerative Rankine cycle branch so that each individual steam generator member may alternately serve as the energy source for the steam cycle.

FIG. 13 is a schematic process diagram of a simplified regenerative Rankine cycle vapor power plant adapted for automotive vehicular applications wherein a maximum expansion piston displacement engine member and a limited expansion turbine engine member are disposed in parallel cycle branches and communicate with a common vapor generator member. The major fraction of cycle working fluid stream discharged from the positive displacement engine member is condensed to liquid in an air-cooled condenser member, and pre-heated by contact interchange with engine-expanded heating vapor within intermediate-pressure contact heat exchangers. The non-condensing turbine engine of FIG. 13 may be used either for overdrive or generation of electrical energy, and exhaust vapor therefrom pre-heats cycle feed liquid by contact interchange within high-pressure contact heat exchangers.

The application of velocity-accelerated contact interchange to the regenerative heating of boiler feed water by low-pressure extracted engine steam in steam power plant processes consists of the following states:

1. Conversion of liquid feed water pressure energy to maximum kinetic energy within nozzle passages of the heat exchanger.

2. Conversion of exhaust or extraction steam kinetic energy to maximum effective pressure energy within diffuser passages of the heat exchanger.

3. Bringing the high-velocity liquid feed water stream and the low-velocity extracted steam fluid stream into physical contact at substantially equal pressure within the mixing section of the heat exchanger while in parallel flow (traveling in the same direction) with respect to each other. The object at this stage is to divide flow within the mixing section of the heat exchanger into fluid laminae having greatly different momenta.

. The large difference in velocity between the two fluid streams accelerates energy transfer between them. Momentum is substantially transferred over an effective mixing length, and accelerates the transfer of thermal energy from the extracted steam over a characteristic length in the mixing section of the heat exchanger.

5. The mixture of condensed and entrained extracted steam together with the high-velocity liquid feed water stream is next guided to a minimumvelocity, maximum pressure state by flowing through a diffuser passage within the heat exchanger.

. The combined fluid streams are next discharged from the heat exchanger and routed into a steam generator or boiler for evaporation.

As indicated earlier herein, the present invention involves a physical and mechanical arrangement of steam power plant process components which effect and facilitate the regenerative feed heating of boiler feed water by extracted engine steam, thereby improving the thermal efficiency of the stream power plant. The teachings of the present invention also involve arrangements which enhance the effectiveness and simplification of steam power plant apparatus.

According to the aforementioned teachings, lowpressure extraction or exhaust engine steam, acting as the heat source to intake liquid feed water passing through the regenerative feed heaters of the process, enters the receiver-plenum of these heat exchangers and is guided to a minimum-velocity, maximum-pressure state in an annular fluid passage surrounding a centrally-mounted liquid feed nozzle member within each heat exchanger. Pressurized and deaerated boiler feed water is supplied to the nozzle passage of the velocity-accelerated contact-type regenerative feed heaters by boiler feed pumps taking suction from the well of a deaerating feed water heater capable of removing air and other entrained gases from the boiler feed condensate.

Within the mixing section of the individual contacttype regenerative feed heaters, extracted steam is combined with the high-velocity feed liquid stream both by entrainment and surface condensation, thereby causing the extracted steam to complete the condensation process in transit and surrender the latent heat of vaporization. The mixture of condensing steam and high-velocity liquid feed water leaves the mixing section of each regenerative feed heater at substantially uniform temperature and is guided through a downstream diffuser passage where kinetic energy is substantially converted to maximum pressure energy. Pre-heated boiler feed water at the approximate saturation enthalpy is discharged from the diffuser passage of the regenerative feed heaters into a collection header, and conveyed to a steam generator or boiler for evaporation downstream of the regenerative feed heaters.

The steam power plant processes referred to before may also employ velocity-accelerated contact-type regenerative feed heaters whose design is the inverse of that described in the preceding two paragraphs. This modified type of regenerative feed heater guides the expansion of the pressurized boiler feed water within an outer annular nozzle passage of the feed heater, and guides the compression of the extracted steam within a central diffuser passage to a minimumvelocity, maximum-pressure state. The aforesaid nozzle and diffuser passageways of the receiver-side section of the regenerative feed heater are adjacent to each other, and separated by a common nozzle-diffuser member. The contact interchange of thermal and kinetic energy takes place within the mixing section of the feed heaters as previously described, after which the preheated mixture of condensed steam and high-velocity feed water has its kinetic energy substantially converted to pressure energy within an annular diffuser passage of the respective heat exchangers. The annular diffuser passage of the feed heaters is formed by the exterior surface of a centrally-mounted coniform flow divider and the interior surface of the annular confining walls of the feed heater, downstream of the mixing section. The pre-heated liquid feed water is next collected and conveyed to a steam generator or boiler for evaporation in the manner previously described.

It should be understood that the terms heat engine and engine include any steam turbine or steam engine ,common to the art.

Referring more particularly to the accompanying drawings, the illustrative embodiment of FIG. 1 shows a steam power plant of the closed-cycle or Rankine-cycle variety which includes improved regenerative feed heating means.

Saturated boiler feed water in the steam drum of forced-circulationstearn generator 10-21 enters suction pipe 11 of circulation pump 12 and is supplied at a higher pressure into discharge main l3. Discharge main 13 of circulating pump 12 is connected to distribution header 14, which is in turn connected to the large plurality of small-diameter steam generating tubes 15. A substantial fraction of the circulating feed water is evaporated within the plurality of steam generating tubes 15 as thermal energy is transferred from the heat ing processes of the steam generator 10-21 to the feed water through the tube walls. The mixture of saturated steam and liquid feed water is combined by the connecting collection header 16, and discharged into steam drum [0 through collection discharge main 17. It

should be understood that saturated steam is separated from the saturated liquid feed water in steam drum 10 by apparatus which is well known in the boiler art.

Saturated steam flows from steam drum 10 of steam generator 1021 through discharge main 18, and enters saturated steam distribution header 19. The saturated steam flows into the large plurality of small-diameter superheat tubes from distribution header 19, and is substantially superheated as thermal energy is transferred to the steam through the walls of superheat tubes 20 from the heating processes of steam generator 10- 21. The superheated steam flows from superheat tubes 20 into superheat collection header 21, which is in turn connected to main steam supply line 22.

It should be understood that the processes described in the preceding two paragraphs are rather common to the art of forced-circulation steam generators, and are internal functions of steam generator 10-21.

The high-energy superheated steam is supplied to steam power turbine 23 from main steam supply line 22, and expanded therewithin. Steam power turbine 23 drives an alternator or other work-absorbing device 25 by shaft member 24. Minor fractions of the total steam flow to steam power turbine 23 are removed from the turbine at extraction orifices 26 and 28, after being substantially expanded therewithin. The major fraction of total steam flow to steam power turbine 23 is expanded within the turbine to a very low pressure, and exhausted into steam condenser 31 through discharge line 30 connecting thereto. The apparatus of steam condenser 31 includes auxiliary equipment which is well known in the art such as the condenser cooling water system, and auxiliary air ejectors, auxiliary condensers and venting apparatus.

The low-pressure exhaust steam is condensed to water within steam condenser 31, as heat energy is removed by the cooling system of the condenser. The condensed steam (or condensate) is collected in the hotwell of condenser 31, and flows into suction line 32 of condensate pump 33. Condensate pump 33 supplies pressurized feed condensate to jet-type deaerating feed water heater 35 through condensate supply main 34.

Jet-type deaerating feed water heater 35 is supplied with low-pressure extracted steam from steam power turbine 23 through extraction orifice 28 and supply pipe 29. The feed condensate is heated by the extracted steam to saturation temperature at the operating pressure of deaerating feed water heater 35, causing the solubility of dissolved gases to become zero. Air and other non-condensable gases are removed from deaerating feed water heater 35 by auxiliary apparatus, using well known techniques. The deaerated feed condensate collects in the hot-well of deaerating feed water heater 35, and flows into suction line 36 connected to distribution header 37 supplying the downstream feed piping system.

Individual members of the plurality of main boiler feed pumps 39 take suction from distribution header 37 through water-jet ejector or eductor 38. Each main boiler feed pump 39 receives the slightly pressurized discharge of deaerated feed water from its companion eductor 38, which in turn takes suction from distribution header 37. Eductor 38 is actuated by the recirculation of a minor fraction of the high-pressure output of its companion main feed pump 39, supplied to the motive nozzle of eductor 38 through recirculation line 40 and throttle valve 41. Operation of throttle valve 41 controls the motive flow of recirculating feed water to eductor 38, and in turn controls the supply pressure to the suction of the respective main feed pump 39. It should be understood that water-jet ejector or eductor 38 acts as a lowpressure feed booster pump to its companion main feed pump 39, and serves to prevent the onset of cavitation within main feed pump 39.

The major fraction of the high-pressure output of each main feed pump 39 is discharged into parallel distribution header 43 through discharge line 42. Parallel distribution header 43 distributes and supplies highpressure feed water to the individual motive nozzle passages of the plurality of water-jet actuated ejectortype regenerative feed heaters 44. The ejector-type regenerative feed heaters 44 take suction from steam distribution header 45, which is supplied with extracted steam from line 27 through steam throttle valve 46. Extracted steam from steam power turbine 23 is supplied to line 27 through extraction orifice 26. It should be noted that the suction flow of heating steam to the plurality of ejector-type regenerative feed heaters 44 is controlled by the operation of steam throttle valve 46.

The mixture of condensed and entrained steam, together with the pre-heated boiler feed water discharged from each ejector-type regenerative feed heater 44 is combined in boiler feed collection header 47. The pre-heated boiler feed water flows from boiler feed collection header 47 into feed supply main 48, and thence into steam drum of steam generator 10-21.

It should be particularly noted that the present invention eliminates the need for closed surface-type regenerative feed heaters in the power generating process of FIG. 1. These closed surface-type regenerative feed heaters contribute considerable cost and complexity to the design of conventional steam power plants. It should also be understood that the need for a closed surface-type economizer pre-heater installation in the upper works of steam generator 10-21 has been eliminated, since feed water is supplied to steam drum 10 at approximately the drum pressure saturation enthalpy.

It should be further noted that auxiliary apparatus and equipment such as feed regulating valves, auxiliary air ejectors and condensers, etc., which do not contribute significantly to an understanding of the schematic process diagram of FIG. 1 have been eliminated therefrom.

FIG. 2 illustrates a fragmentary longitudinal section of a conventional water-jet actuated ejector-type regenerative feed heater such as is indicated schematically at 44 on FIG. 1. High-pressure feed water is received from the main boiler feed pumps through feed supply pipe 56, connected to annular nozzle member 54. Annular nozzle member 54 is fitted with annular flange member 55, and centrally-mounted within the shell of receiving chamber 52. Receiving chamber 52 is fitted with annular entrance flange 51 and annular exit flange 53, and is fabricated by casting or other suitable means. Receiving chamber 52 is supplied with lowpressure extracted steam from steam supply pipe 49 through the connected annular pipe socket flange 50 affixed to the supply pipe and annular entrance flange 51 of the receiving chamber. Diffuser section 62, housing diffuser passage 64, is fitted with annular entrance flange 61 and annular exit flange 63. Annular entrance flange 61 of diffuser section 62 connects to exit flange 53 of receiving chamber 52 by bolting or other suitable means, while the exit flange 63 is similarly connected to the adjacent annular pipe socket flange 65. Preheated boiler feed water is discharged from the regenerative feed heater 51-63 through discharge pipe 66, which is connected to annular pipe socket flange 65.

High-pressure feed water is supplied to nozzle passage 57 of annular nozzle member 54 from feed supply pipe 56, and expanded within the nozzle passage to a high-velocity low-pressure state. Low-pressure extracted steam is diffused to a low-velocity within fluid passage region 58 of receiving chamber 52, the same fluid passage region surrounding centrally-mounted annular nozzle member 54. The high-velocity particles of the feed liquid stream leave nozzle passage 57 and assume intimate contact with the low-velocity particles of extracted steam within receiving chamber 52 at substantially equal pressures. The preliminary mixing of low-velocity steam and high-velocity feed liquid takes place substantially within the confines of mixing section 60, which is indicated in phantom.

The contact interchange of thermal and kinetic energy between the high-velocity feed liquid stream and the low-velocity extracted steam fluid streams takes place in parallel flow, and is initiated within mixing section 60. Substantial combination of the feed liquid and extracted steam occurs both by surface condensation upon the high-velocity particles of the feed liq uid stream, and by entrainment through momentum transfer between the fluid streams. Entrained extracted steam particles are substantially condensed as the pressure of the combined streams is increased through velocity reduction in diffuser passage 64. The preheated and combined feed water stream is discharged from diffuser passage 64 into discharge pipe 66 at the approximate saturation enthalpy for the pressure of the downstream steam generator or boiler.

FIG. 3 depicts a partial schematic diagram of a steam power generating process similar to FIG. 1, wherein a plurality of inverted velocity-accelerated contact-type regenerative feed heaters 67 are substituted for the more conventional ejector-type regenerative feed heaters 44 of FIG. 1. Deaerated feed water is received from deaerating feed water heater 35 and supplied under high pressure to parallel distribution header 43 in the manner previously described. Extracted steam from the upstream steam power turbine is supplied to each regenerative feed heater 67 from steam distribution header 45 as before. The heat content of the several fluid streams is substantially combined within each regenerative feed heater 67 and discharged into boiler feed collection header 47. Boiler feed collection header 47 supplies pre-heated feed water to steam drum 10 of steam generator 10-21 through feed supply main 48, exactly as described for the steam power plant process of FIG. 1.

FIGS. 4, 5, 6 and 7 depict fragmentary sections of the inverted regenerative feed heater indicated schematically at 67 on FIG. 3.

High-pressure feed water is received from the main feed pumps through feed supply pipe 69. Feed supply pipe 69 is connected to concentric line enlarger section 70, connected to annular pipe socket flange 71. Annular pipe socket flange 71 is connected by bolting or other suitable means to the adjacent annular pipe socket flange 72, which is in turn connected to the adjacent exchanger pipe wall 73. Heat exchanger -87 is supplied with extracted steam from steam supply pipe 68, extending through exchanger pipe wall 73 as shown. Exchanger pipe 73 is connected to annular pipe socket flange member at its discharge end. Annular pipe socket flange 85 is connected by bolting or other suitable means to the adjacent annular pipe socket flange 86, which is in turn connected to concentric line reducer section 87. Exchanger discharge pipe 88 is connected to concentric line reducer section 87 as 9 shown, and carries the pre-heated and combined feed discharge from heat exchanger 7087 to processes down stream of the heat exchanger.

Exchanger pipe 73 of heat exchanger 70-87 houses fittings which facilitate the velocity-accelerated contact interchange processes. Concentrically mounted within exchanger pipe 73 is annular nozzle-diffuser member 74 of substantially frusto-conical shape. Annular nozzle-diffuser member 74 is stabilized within exchanger pipe 73 by intermediately disposed bracket or spider members 75. The internal diffuser passage 77 of annular nozzle-diffuser member 74 is supplied with extracted steam from steam supply pipe 68, which is connected to the smaller end of annular nozzle-diffuser 74 as shown. Annular nozzle passage 76 is defined by the exterior surface of annular nozzle-diffuser member 74 and the interior walls of exchanger pipe member 73. Annular nozzle passage 76 serves to guide the expansion of high-pressure feed water to a high-velocity lowpressure state within heat exchanger 70-87.

Concentrically mounted within exchanger pipe 73 .and disposed downstream of annular nozzle-diffuser member 74 is coniform flow divider 80. Coniform flow divider 80 is stabilized at its leading end by intermediately disposed bracket or spider members 81, disposed obliquely of and secured to the exit section of annular nozzle-diffuser member 74. The trailing end of coniform flow divider 80 is stabilized by interrnediately disposed bracket or spider members 82, secured to the exchanger pipe walls 73 as shown.

The contact interchange of thermal and kinetic energy between the low-velocity extracted steam and the high-velocity feed water fluid streams is initiated along the interface between the annular fluid passage regions 78 and 79 respectively. This preliminary mixing with turbulent flow is indicated by the short curled lines downstream of nozzle-diffuser member 74 on FIG. 4, and is substantially completed within the confines of mixing section 83 (indicated in phantom). After leaving mixing section 83 the combined fluid streams flow into annular diffuser passage 84, where entrained steam is further condensed as pressure increases with decreasing velocity. Annular diffuser passage 84 is defined by the exterior surface of coniform flow divider 80, together with the interior walls of exchanger pipe 73 and concentric line reducer section 87. The preheated feed liquid flows from annular diffuser passage 84 into exchanger discharge pipe 88, and thence to the downstream steam generator or boiler.

Velocity-accelerated contact heat exchanger arrangements may be advantageously varied within the closed-cycle, regenerative Rankine power plant process configuration described hereinbefore. As shown in FIG. 8, a plurality of velocity-accelerated contact heat exchangers may be supplied with motive feed water at a common supply pressure and individual contact heat exchangers receive extracted turbine heating steam at different pressures while all the contact heat exchangers discharge to a common boiler supply pressure.

Referring to FIG. 8, high-pressure steam supplied by an upstream steam generator or boiler enters steam power turbine -90 from main steam supply line 89 and expands therewithin. Steam power turbine 90 drives an alternator or other work-absorbing device 92 by shaft member 91. Minor fractions of the total steam flow to steam power turbine 90 are discharged from the turbine at successively lower pressures through extraction orifices 93, 95, 97 and 99 after substantial expansion within. The major fraction of total steam flow to turbine 90 is expanded within to a very low pressure, and exhausted into steam condenser 102 through discharge line 101 connected thereto. The apparatus of steam condenser 102 includes auxiliary equipment well known in the art such as the condenser cooling water system, and auxiliary air ejectors, auxiliary condensers and venting apparatus.

The low-pressure exhaust steam is condensed to water within steam condenser 102. The liquid condensate is collected in the hotwell of condenser 102, and flows into suction line 103 of condensate pump 104. Condensate pump 104 supplies pressurized feed con densate to jet-type deaerating feed water heater 106 through condensate supply line 105.

Jet-type deaerating feed water heater 106 is supplied with low-pressure extracted steam from steam power turbine 90 through extraction orifice 99 and supply line 100. Air and non-condensable gases are removed from the feed condensate in deaerating feed water heater 106 using well known apparatus and techniques. The deaerated feed condensate collects in the hotwell of deaerating feed water heater 106, and flows through discharge line 107 into distribution header 108.

Individual members of the plurality of main boiler feed pumps 110 take suction from. condensate distribution header 108 through water-jet ejector or eductor 109. Feed condensate entering the suction of each individual feed pump 110 is slightly pressurized by eductor 109. Eductor 109 is actuated by pressurized feed water recirculated from the discharge of feed pump 110 through recirculation line 111 and throttle valve 112. The major fraction of pressurized feed water discharged by feed pumps 110 enters feed water collection-and-distribution header 114. Pressurized feed water is supplied from collection-and-distribution header 114 to individual nozzle passages of the plurality of ejector-type contact heat exchangers 116, 120 and 124.

Individual contact heat exchanger member 116 is supplied with low-pressure turbine heating steam through extraction orifice 97 by way of steam line 98 and throttle valve 117. Low-pressure turbine heating steam supplied through extraction orifice 97 is at a lower pressure than that supplied through extraction orifices 93 and 95. The pressure energy of motive fluids supplied by pumps to contact heat exchanger 116 is largely converted to kinetic energy to facilitate the contact interchange process. Individual contact heat exchanger member 116 discharges to boiler feed water collection header 127, the same having boiler feed supply line 128 af'fixed thereto.

Individual contact heat exchanger member 120 is supplied with low-pressure turbine heating steam through extraction orifice 95 by way of steam line 96 and throttle valve 121. Low-pressure turbine heating steam supplied through extraction orifice 95 is at an intermediate pressure between that supplied through extraction orifices 93 and 97. The pressure energy of motive fluids supplied by pumps 1110 to contact heat exchanger 120 is partially converted to kinetic energy to facilitate the contact interchange process. Individual contact heat exchanger member 120 discharges to boiler feed water collection header 127, the same having boiler feed supply line 128 affixed thereto.

Individual contact heat exchanger member 124 is supplied with low-pressure turbine heating steam through extraction orifice 93 by way of steam 94 and throttle valve 125. Low-pressure turbine heating steam supplied through extraction orifice 93 is at a higher pressure than that supplied through extraction orifices 95 and 97. The pressure energy of motive fluids supplied by pumps 110 to contact heat exchanger 124 is partly converted to kinetic energy to facilitate the contact interchange process. Individual contact heat exchanger member 124 discharges to boiler feed water collection header 127, the same having boiler feed supply line 128 affixed thereto.

Velocity-accelerated contact heat exchanger configurations may be further varied within the closedcycle regenerative Rankine steam power plant process described hereinbefore. As shown in FIG. 9, a plurality of contact heat exchangers may be supplied with motive feed water at a common pressure and discharge pre-heated feed water to the common boiler supply pressure, while each contact heat exchanger member independently receives low-pressure extracted heating steam from a separate steam turbine member which is supplied by the common steam generator or boiler member.

Referring to FIG. 9, high-pressure steam is supplied by an upstream steam generator or boiler member to distribution header 130 through steam supply main 129. Distribution header 130 communicates with main steam power turbine supply branch 131 and with auxiliary steam turbine supply branch 140.

High-pressure steam enters main steam turbine 132 from supply branch 131 and expands therewithin. Turbine 132 drives alternator or other work-absorbing device 134 by shaft member 133. Minor fractions of the total steam flow to main steam power turbine 132 are discharged from the turbine at successively lower pressures through extraction orifices 135 and 137, after substantial expansion therewithin. The major fraction of total steam flow to turbine 132 is expanded within to a very low pressure, and exhausted into main steam condenser 152 through discharge line 139 connected thereto. Main steam condenser 152 includes auxiliary supporting equipment common to the surface condenser art.

The low-pressure exhaust steam from turbine 132 is condensed to water within steam condenser 152. The hotwell of condenser 152 also receives the condensate of auxiliary condenser 148 from discharge line 151 and auxiliary condensate pump 150. The condensate in the hotwell of steam condenser 152 flows into suction line 153 of main condensate pump 154. Main condensate pump 154 supplies pressurized feed condensate to jettype deaerating feed water heater 156 through condensate supply line 155.

High-pressure steam from distribution header 130 enters auxiliary steam turbine supply branch 140, the same having pressure-reducing valve 141 disposed therein. The steam supply to auxiliary steam turbine 142 is provided at a useful working pressure for the turbine by expansion in pressure-reducing valve 141, and

then further expanded within the turbine. Auxiliary turbine 142 drives alternator or other work-absorbing device 144 by shaft member 143. A minor fraction of the total steam flow to auxiliary steam turbine 142 is discharged from extraction orifice 145 after substantial expansion therewithin. The major fraction of total steam flow to auxiliary turbine 142 is expanded within to the exhaust pressure, and discharged into auxiliary steam condenser 148 through discharge line 147 connected thereto. The exhaust steam of auxiliary turbine 142 is condensed to liquid within auxiliary condenser 148, and flows from the condenser hotwell into suction line 149 of auxiliary condensate pump 150. The auxiliary feed condensate is discharged by pump 150 into the hotwell of main steam condenser 152 through condensate line 151.

Jet-type deaerating feed water heater 156 is supplied with low-pressure extracted steam from main steam power turbine 132 through extraction orifice 137 and supply line 138. Air and non-condensable gases are removed from the feed condensate in deaerating feed water heater 156. The deaerated feed condensate flows from the hotwell of heater 156 into distribution header 158 through discharge line 157.

Individual members of the plurality of main boiler feed pumps take suction from condensate distribution header 158 through water-jet ejector or eductor 159. Feed condensate entering the suction of each individual feed pump 160 is slightly pressurized by eductor 159. Eductor 159 is actuated by pressurized feed water recirculated from the discharge of feed pump 160 through recirculation line 161 and throttle valve 162. The major fraction of pressurized feed water discharged by feed pumps 160 enters feed water collection-and-distribution header 164 through discharge line 163. Pressurized feed water is supplied from collection-and-distribution header 164 to individual nozzle passages of the plurality of ejector-type contact heat exchangers 166 and 170.

Individual contact heat exchanger member 166 is supplied with low-pressure heating steam through extraction orifice 145 of auxiliary steam turbine 142 by way of steam line 146 and throttle valve 167. Pressure energy of motive fluid supplied by feed pumps 160 is substantially converted to kinetic energy within heat exchanger 166 to facilitate the contact interchange process. Ejector-type contact heat exchanger 166 discharges pressurized boiler feed water through discharge line 168 into collection header 173, the same having boiler feed supply main 174 connected thereto.

Individual contact heat exchanger member 170 is supplied with low-pressure heating steam through extraction orifice 135 of main steam turbine 132 by way of steam line 136 and throttle valve 171. Pressure energy of motive fluid supplied by feed pumps 160 is substantially converted to kinetic energy within heat exchanger 170 to facilitate the contact interchange process. Ejector-type contact heat exchanger 170 discharges pressurized boiler feed water through discharge line 172 into collection header 173, the same having boiler feed supply main 174 connected thereto.

In another regenerative Rankine variation adapted for very high-pressure cycles, the boiler feed water may be heated within a contact heat exchanger to nearly the saturation enthalpy for an intermediate cycle pressure using extracted turbine steam. The boiler feed water is then raised to a higher pressure by another set of feed pumps, and heated within additional contact heat exchangers to nearly the saturation enthalpy for a higher cycle pressure. This series-connected arrangement of feed pumps and contact heat exchangers may be used to limit erosive damage to motive nozzles of the contact heat exchangers which could be caused by converting excessive amounts of pressure energy to kinetic energy therewithin.

Referring to FlG. 10, high-pressure steam is supplied by an upstream steam generator or boiler member to main steam power turbine 176 through steam supply mam 175.

High-pressure steam enters turbine l'76 and expands therewithin. Turbine 1'76 drives alternator or other work-absorbing device 178 by shaft member 177. Minor fractions of total steam flow to power turbine 176 are discharged from the turbine at successively lower pressures through extraction orifices 179, 181i and 183 after substantial expansion therewithin. The major fraction of total steam flow to turbine 1176 is expanded within to a very low pressure, and exhausted into main steam condenser 186 through discharge line 185. Steam condenser 186 includes auxiliary supporting equipment common to the surface condenser art.

The low-pressure turbine exhaust steam is condensed to water in condenser 186 and flows into suction line 187 of condensate pump 138. Condensate pump 188 discharges pressurized feed condensate to jet-type deaerating feed water heater 190 through discharge line 189. Deaerating feed water heater 190 is supplied with low-pressure extracted steam from turbine 176 through extraction orifice 183 and supply line 184. The

deaerated feed condensate flows from deaerating feed heater 1% into distribution header 192 through discharge line 191.

lndividual members of the plurality of motive feed pumps 1% take suction from condensate distribution header 192 through water-jet ejector or eductor 1%. Feed condensate entering the suction of an individual feed pump B94 is slightly pressurized by eductor I193. Eductor l93 is actuated by a recirculated minor fraction of the pressurized feed discharge of pump 11% through recirculation line W and throttle valve we. The major fraction of pressurized feed water from pump 1% enters collection-and-distribution header 1% through discharge line 1197. The pressurized feed discharge is supplied to nozzle passageways of the plurality of ejector-type contact heat exchangers 2% through motive feed supply line 199.

Ejector-type contact heat exchanger members 2% are supplied with intermediate pressure extracted heating steam from turbine 176 through extraction orifice 181, supply line 382 and regulating throttle valve 2M. The extracted intermediate pressure heating steam enters contact heat exchanger 2% from distribution header 202. The heated intermediate pressure feed water passes from contact heat exchanger 200 into collection-and-distribution header 2% through discharge line 203.

Individual members of the plurality of motive feed pumps 2W7 talte suction from collection-and-distribution header 204 through water-jet ejector and eductor 2.06 and suction line 2%. Saturated feed condensate entering the suction of an individual feed pump is slightly pressurized by educator 21%. Eductor 206 is actuated by a recirculated minor fraction of pressurized feed water discharge of pump 207 through recirculation line 2% and throttle valve 269. The major fraction of feed water iirom pumps 2W7 enters collection-anddistribution header Ell through discharge line 210. The pressurized feed discharge is supplied to nozzle passageways of the pluralityof ejector-type contact heat exchangers 213 through motive feed supply line 212.

Ejector-type contact heat exchanger members 213 are supplied with high-pressure extracted heating steam from turbine i176 through extraction orifice T79, supply line lhll and regulating throttle valve Md. The extracted high-pressure heating steam enters contact heat exchangers 2T3 from distribution header 215. The heated high-pressure feed water is discharged from contact heat exchangers 2T3 intothe upstream steam generator or boiler member through collection header 217 and boiler feed supply line 21h.

Another combinative regenerative Rankine cycle variation is adapted for multiple steam power plant system to be used aboard ship or certain industrial power plants. in this variation a plurality of contacttype Rankine cycle branches are connected in parallel with respect to each other and a common steam generator so that any steam cycle branch may alternately be connected to form a separate regenerative steam cycle with the common steam generator member. in a practical installation one discreet steam cycle branch in one of several engine rooms might be alternately connected to the steam generator in any one of several adjacent tirerooms to form a separate regenerative Rankine steam cycle.

in H6. ill, the right-hand steam cycle branch ZZZl-Zdd is receiving high'pressure steam from a common upstream steam generator member as flow proceeds in the directions shown by the exterior arrows. While the righthand steam cycle branch int-Edd is in use, the alternate left-hand steam cycle branch amass is idle due to isolation by steam valve 222 or other valves common to the steam power plant art (not shown).

High-pressure steam from the common upstream steam generator enters turbine 223 of the active right hand steam cycle branch by way of steam main 2T9, main steam header 2%, and open right-hand steam supply valve 222 and expands within the turbine. Turbine 223 drives alternator or other work-absorbing device 225 by shaft member 22d. Minor fractions of total steam flow to power turbine: 223 are discharged from low-pressure extraction orifices 22.6 and 228. The major fraction of total steam flow to turbine 2.23 is expanded to a very low exhaust pressure and flows into steam condenser 2.311 through discharge line .230.

The condensate flows from condenser 2311. into suction line 232 of condensate pump 233, and is discharged under pressure into deaerating feed water heater 235 via discharge line 233d. Low-pressure extracted heating steam from turbine 22.3 enters deaerating feed water heater 23th" by way of supply line 229 and extraction orifice 22th. The deaerated feed condensate flows from heater 235 into discharge line 23b and dis tribution header 237.

Individual members of the plurality of motive feed pumps 239 take suction from condensate distribution header 237 through water-jet ejector or eductor 238. Eductor 238 is actuated by a recirculated minor fraction of the pressurized output of feed pump 239 through recirculation line 240 and throttle valve 241, and slightly pressurizes the feed condensate above the saturation pressure. The major fraction of pressurized feed water from pump 239 enters collection-and-distribution header 243 through discharge line 242. The pressurized feed water flows from collection-and-distribution header 243 into nozzle passageways of the plurality of ejector-type contact heat exchanger 244.

Ejector-type contact heat exchangers 244 are supplied with low-pressure extracted heating steam from turbine 223 through extraction orifice 226, supply line 227, regulating steam throttle valve 246 and distribution header 245. The heated feed water is discharged from plurality of contact heat exchangers 244 into distribution header 247 and feed supply line 248. Feed supply line 248 communicates withthe common steam generator member for both the right-hand and lefthand steam cycle branches.

Feed supply lines 248 from both the right-hand and left-hand steam cycle branches may be combined together before communicating with the common steam generator member. Alternately feed supply lines 248 from both the right-hand and left-hand steam cycle branches may communicate separately with the common steam generator as convenient.

A further combinative regenerative Rankine cycle variation is specially adapted for multiple steam power plant system use aboard ship or in certain industrial power plants. In this variation a plurality of individual steam generator members are connected in parallel with respect to each other and a common contact-type regenerative Rankine cycle branch so that any steam generator member may be alternately connected to form a separate regenerative steam cycle with the common steam cycle branch. In a practical installation, one steam generator member in one of several firerooms might be alternately connected to a common steam cycle branch in any of several adjacent engine-rooms to form a separate regenerative steam cycle.

In FIG. 12 the right-hand steam generator member 249-260 is providing high-pressure steam to the common steam cycle branch 264-290 as flow proceeds inthe direction shown by the exterior arrows. When the right-hand steam generator 249-260 is in active use, the alternate steam generator member 249-260 is idle and isolated by closure of the respective steam valve 262 and feed valve 293 or other valves common to the steam power plant art.

Steam generator member 249-260 is composed of steam drum 249, circulating pump suction line 250, circulating pump 251, pump discharge line 252, distribution header 253, evaporator tubes 254, collection header 255, saturated steam-and-water discharge line 256, saturated steam discharge line 257, distribution header 258, superheat tubes 259 and superheat collection header 260. Steam generator member 249-260 functions similarly as steam generator member -21 of FIG. 1.

Common steam cycle branch 264-289 of FIG. 12 is composed of steam supply main 264, steam turbine 265, shaft member 266, alternator or other work absorber 267, high-pressure extraction orifice 263, highpressure extracted steam line 269, low-pressure extraction orifice 270, low-pressure extracted steam line 271, turbine discharge line 272, steam condenser 273, pump suction line 274, condensate pump 275, condensate supply main 276, deaerating feed water heater 277, discharge line 278, distribution header 279, eductors 280, feed pumps 281, recirculation lines 282, throttle valves 283, pump discharge lines 284, collection-anddistribution header 285, contact heat exchangers 286,

steam distribution header 287, steam throttle valve" 288, and feed water collection header 289. The common steam cycle branch 264-289 of FIG. 12 and elements thereof functions similarly as steam cycle branch 22-47 of FIG. 1 and the respective elements thereof.

High-pressure steam from the active right-hand steam generator member 249-260 of FIG. 12 is supplied to the common contact-type regenerative Rankine steam cycle branch 264-289 by way of steam supply branch 261, open steam valve 262 and distribution header 263. The high-pressure steam then enters steam turbine 265 from supply main 264, and is expanded therewithin.

Pre-heated feed water from contact heat exchangers 286 flow from feed water collection header 289 into feed main 290 and feed water distribution header 291. The pre-heated pressurized feed water is supplied thence to the active steam generator member 249-260 from feed water distribution header 291 by way of feed supply branch 292 and feed valve 293.

Another regenerative Rankine cycle variation of the invention is a multi-engine combination for application to automotive or other mobile power plant systems. This mobile power plant variation may use any cycle working fluid having useful thermodynamic properties, such as water or various organic fluids. This mobile regenerative Rankine vapor cycle includes among its apparatuses a common vapor generator member, a common air-cooled vapor-to-liquid condenser member for condensing low-pressure engine exhaust vapor, an individual non-positive displacement vapor turbine member and a positive-displacement engine member connected in parallel with respect to each other and with respect to both the common vapor generator member and the common air-cooled condenser member, and a plurality of contact heat exchangers to pre-heat the cycle working fluid before vaporization by contact interchange with low-pressure engine exhaust vapors. In an automotive power plant application the positive displacement engine member would have maximum operating advantages during stop-and-go driving or other driving at variable vehicle speeds, while the non-positive displacement turbineengine member would have maximum operating advantage during highway cruising at more nearly constant vehicle speed.

In the simplified vapor cycle schematic diagram of FIG. 13, both turbine engine member 301 and pistontype displacement engine member 309 may be operated jointly together to collectively provide vehicle power. Either turbine engine member 301 or pistontype displacement engine member 309 may also be operated singly to provide power for the vehicle. For example reciprocating piston engine member 309 may be designed to provide motive power at all vehicle speeds, while turbine engine member 301 could be designed as an overdrive unit which is clutched in to help drive the vehicle during highway cruising. In a system of the latter type output shaft members of both the turbine engine member 301 and the displacement engine member 309 may each be individually connected to the same vehicle load by variable-speed fluid couplings, or other suitable means which enables either engine member to drive the vehicle separately or permits both engines to drive the vehicle jointly together. Alternately, turbine engine member 301 might be designed to drive an alternator for development of electrical power, while all motive power is developed by piston-type displacement engine member 309.

In FIG. 13 monotube vapor generator 294 includes integral air supply fan 295, fuel supply line 296 and combustion gas outlet line 297. High-pressure vapor is discharged from vapor generator 294 into supply header 298, and flows thence into turbine engine vapor supply branch 299 and piston displacement engine vapor supply branch 305.

The admission of high-pressure vapor into turbine engine 301 from supply branch 299 is regulated by operation of throttle valve 300. The high-pressure vapor is partially expanded within turbine engine 301 and discharged through exhaust branch 303 having valve 304. Turbine engine member 301 may drive any work-absorbing device in the vehicle power system by connection to output shaft member 302.

The admission of high-pressure vapor flowing into piston-displacement engine 309 from supply branch 305 through open valve 306 past closed bypass valve 338 and supply branch 307 through throttle valve 308 is regulated by adjustment of throttle valve 308. The high-pressure vapor is expanded within cylinders of engine 309 to a low-pressure state, and leaves the engine through exhaust main 313. Piston displacement engine 309 may drive the vehicle by suitable transmitting means connected to output shaft member 310. Piston displacement engine 309 also drives propeller fan 312 by auxiliary shaft member 311 to provide forced convective cooling for vapor-to-liquid condenser 315. The major fraction of total vapor flow to piston displacement engine 309 is expanded to a low pressure and discharged into air-cooled vapor-to-liquid condenser 315 through exhaust vapor inlet branch 314.

Vapor-to-liquid condenser 315 is cooled by forced connection from the air stream supplied by enginedriven propeller fan 312. Air-cooled condenser 315 includes extended heat transfer surface common in the heat exchanger arts. The condensed liquid phase of the cycle working fluid drains from condenser 315 into the suction of condensate pump 317 through condenser discharge line 316, and is discharged by condensate pump 317 unto surge tank 319 through discharge line 318. Surge tank 319 provides necessary reserve storage capacity for the working fluid liquid phase required to compensate for fluctuations in the power demand of a mobile vehicle. The liquid condensate flows from surge tank 319 into suction line 320 of first-stage feed pump 321. Pressurized feed liquid is discharged by feed pump 321 into feed discharge main 322, and flows into motive-nozzle distribution header 323 for supply to the plurality of contact heat exchangers 324.

A minor fraction of low-pressure exhaust vapor from piston displacement engine 309 is discharged into exhaust heating main 326. Exhaust heating main 326 includes regulating throttle valve 327 and communicates with exhaust vapor distribution header 325 for supply of heating vapor to the plurality of contact heat exchangers 324. Adjustment of throttle valve 327 re gulates admission of heating vapor into contact heat exchangers 324.

The heated discharge of feed liquid from contact heat exchangers 324 enters feed collection header 328 and flows through feed suction main 329 into secondstage feed pump 330. Pressurized feed liquid from feed pump 330 flows through heat feed discharge main 331 into motive-nozzle distribution header 332 for supply to the plurality of contact heat exchangers 333.

Exhaust vapor from turbine engine 301 may flow through exhaust branch 303 through valve 304, past closed bypass valve 338, and exhaust discharge branch 335 through throttle valve 336. Exhaust discharge branch 335 communicates with exhaust distribution header 334 for the supply of heating vapor to the plurality of second-stage contact heat exchangers 333. Throttle valve 336 may be operated in the open position when the total vapor flow to turbine engine 301 requires complete mixing with the condensed liquid phase of the cycle working fluid. Throttle valve 336 may also be adjusted to regulate the admission of heating vapor into contact heat exchangers 333 when alternate cycle branch adjustments are made.

The heated discharge of feed liquid from contact heat exchangers 333 enters feed collection header 339, and thence flows into feed supply main 340 of monotube vapor generator 294.

Several alternate operating arrangements may be made to the power plant system of FIG. 13 by making appropriate valve adjustments in various piping branches. Bypass branch 337 having bypass valve 338 communicates with displacement engine vapor supply branches 305 and 307, and with turbine engine exhaust branch 303 and exhaust discharge branch 335. For example, if turbine engine supply throttle valve 300 and exhaust valve 304 were closed off, all vapor flow from generator 294 would pass through supply branch 305. Admission of secondary heating vapor to second-stage contact heat exchangers 333 would be regulated by adjustment of throttle valve 336, after the secondary heating vapor flows through open bypass valve 338.

It should be understood that the simplified piping system of FIG. 13 may include branches or apparatus not shown, but required as common practice in the power plant art to provide operating flexibility. For example, a valved bypass branch connection between motive-nozzle distribution header 323 and feed collection header 328 would normally be provided, to bypass contact heat exchangers 324 during start-up. Similarly, a valved bypass branch connection between motivenozzle distribution header 332 and feed collection header 339 may be provided to bypass second-stage contact heat exchangers 333. Cross connection between the aforesaid bypass branches may also be made with advantage. Other minor alterations are possible, within the ordinary practice of piping arts, which would not affect the combinative vapor power plant system of FIG. 13.

From the foregoing, it will be perceived by those skilled in the art that the present process invention provided an efficient means of effecting regenerative feed water heating in a steam power plant. In addition, the use of velocity-accelerated contact-type regenerative feed heaters in the steam power plant process makes possible a considerable simplification of steam power plant cycles through the elimination of closed surfacetype heat exchangers for the pre-heating of boiler feed water.

While I have shown and described certain specific embodiments of the present process invention, it will be readily understood by those skilled in the art that I do not wish to be limited exactly thereto, since various modifications may be made without departing from the scope of the invention as defined in the appended claims.

I CLAIM:

l. Regenerative feed heating means impressed upon the thermo-dynamic processes of a vapor power plant comprising in combination: a vapor generator having integral heating processes; a heat engine member adapted to expand heated and pressurized working fluid supplied from said vapor generator member; means for transferring heated and pressurized working fluid from the said vapor generator to the inlet of said heat engine member; a fluid-to-fluid contact heat exchanger adapted to effect the regenerative pre-heating of high-velocity feed liquid by contact interchange in parallel flow with low-velocity expanded heating vapor by means of accelerating nozzle and ejector passageways internally disposed within said contact heat exchanger member; a supply of feed liquid suitable for evaporation within said vapor generator member; a liquid feed pump; means for transferring the said supply of feed liquid to the suction of said feed pump; means for transferring pressurized feed liquid from said feed pump to a nozzle passageway of said contact heat exchanger; a source of expanded heating vapor suitable for combination with the said feed liquid; means for transferring the said expanded heating vapor to the ejector passage of said contact heat exchanger; valve regulating means disposed to control flow of the said expanded heating vapor into the ejector passageway of said contact heat exchanger to regulate heat absorption by feed liquids passing therethrough; and means for transferring the heated feed liquid discharge of said contact to heating processes of said vapor generator member; the said contact heat exchanger being adapted to receive and exchange energy between high-velocity feed liquid and expanded heating vapor in parallel flow within internal fluid passageways thereof, to combine the thermal energy of the several entering fluid streams, and to discharge pressurized and pre-heated feed liquid from a diffuser passageway thereof; whereby the external effect of the regenerative feed heating process is to pre-heat feed liquid by contact interchange with expanded heating vapor, thereby decreasing the quantity of heat energy supplied by the said vapor generator member to raise the temperature of the feed liquid to the saturation temperature at the pressure of the evaporation process.

2. The general regenerative power plant of claim 1 wherein a plurality of fluid-to-fluid contact heat exchangers are disposed in parallel with respect to each other between common pressurized feed liquid and expanded heating vapor supply headers, and dischargers pre-heated feed liquid from said contact heat exchangers to heating processes of said vapor generator member.

3. The general regenerative power plant of claim 1 wherein expanded heating vapor supplied from said contact heat exchanger is discharged from processes provided with heated and pressurized vapor from said vapor generator member.

4. The general regenerative power plant of claim 1 wherein the contact heat exchanger is comprised by an ejector having a centrally-disposed nozzle passage surrounded by an outer ejector passage in the receiving section thereof, and discharges the combined fluid streams through a diverging frusto-conical diffuser passage.

5. The general regenerative power plant of claim 1 wherein the contact heat exchanger is comprised by an ejector having a centrally-disposed ejector passage surrounded by an outer nozzle passage in the receiving section thereof, and discharges the combined fluid streams through a diverging annular diffuser passage.

6. Regenerative feed heating means impressed upon the thermo-dynamic processes of a Rankine cycle power plant comprising in combination: a vapor generator having integral heating processes; a heat engine member adapted to expand the cycle working fluid; a vapor-to-liquid condenser member adapted to receive expanded vapor from a discharge outlet of said heat engine member and to condense said expanded vapor to liquid by transfer of heat energy therefrom; an ejector-type fluid-to-fluid contact heat exchanger adapted to effect the regenerative pre-heating of high velocity feed liquid by contact interchange in parallel flow with expanded heating vapor from a discharge outlet of the said heat engine member; a liquid feed pump; communicating means between the outlet of said vapor generating member and the inlet of said heat engine member for the transfer of heated and pressurized cycle working fluid; communicating means between a discharge outlet of said heat engine member and the inlet of said condenser member for the transfer of expanded cycle working fluid; communicating means between the liquid outlet of said condenser member and the inlet of said feed pump; communicating means between the discharge of said feed pump and accelerating nozzle passageways of said contact heat exchanger; communicating means between a discharge outlet of said heat engine member and ejector passageways of said contact heat exchanger for the transfer of expanded heating vapor; valve regulating means disposed to control flow of the said expanded heating vapor from a discharge outlet of said heat engine member into ejector passageways of said contact heat exchanger to regulate heat absorption by feed liquids passing therethrough; and communicating means between the fluid discharge of said contact heat exchanger and heating processes of said vapor generator member; the said contact heat exchanger being adapted to receive and exchange energy between highvelocity feed liquid and engine-expanded heating vapor in parallel flow within internal fluid passageways thereof, to combine the thermal energy of the several entering fluid streams, and to discharge pressurized and 

1. Regenerative feed heating means impressed upon the thermodynamic processes of a vapor power plant comprising in combination: a vapor generator having integral heating processes; a heat engine member adapted to expand heated and pressurized working fluid supplied from said vapor generator member; means for transferring heated and pressurized working fluid from the said vapor generator to the inlet of said heat engine member; a fluid-to-fluid contact heat exchanger adapted to effect the regenerative pre-heating of high-velocity feed liquid by contact interchange in parallel flow with low-velocity expanded heating vapor by means of accelerating nozzle and ejector passageways internally disposed within said contact heat exchanger member; a supply of feed liquid suitable for evaporation within said vapor generator member; a liquid feed pump; means for transferring the said supply of feed liquid to the suction of said feed pump; means for transferring pressurized feed liquid from said feed pump to a nozzle passageway of said contact heat exchanger; a source of expanded heating vapor suitable for combination with the said feed liquid; means for transferring the said expanded heating vapor to the ejector passage of said contact heat exchanger; valve regulating means disposed to control flow of the said expanded heating vapor into the ejector passageway of said contact heat exchanger to regulate heat absorption by feed liquids passing therethrough; and means for transferring the heated feed liquid discharge of said contact to heating processes of said vapor generator member; the said contact heat exchanger being adapted to receive and exchange energy between highvelocity feed liquid and expanded heating vapor in parallel flow within internal fluid passageways thereof, to combine the thermal energy of the several entering fluid streams, and to discharge pressurized and pre-heated feed liquid from a diffuser passageway thereof; whereby the external effect of the regenerative feed heating process is to pre-heat feed liquid by contact interchange with expanded heating vapor, thereby decreasing the quantity of heat energy supplied by the said vapor generator member to raise the temperature of the feed liquid to the saturation temperature at the pressure of the evaporation process.
 2. The general regenerative power plant of claim 1 wherein a plurality of fluid-to-fluid contact heat exchangers are disposed in parallel with respect to each other between common pressurized feed liquid and expanded heating vapor supply headers, and dischargers pre-heated feed liquid from said contact Heat exchangers to heating processes of said vapor generator member.
 3. The general regenerative power plant of claim 1 wherein expanded heating vapor supplied from said contact heat exchanger is discharged from processes provided with heated and pressurized vapor from said vapor generator member.
 4. The general regenerative power plant of claim 1 wherein the contact heat exchanger is comprised by an ejector having a centrally-disposed nozzle passage surrounded by an outer ejector passage in the receiving section thereof, and discharges the combined fluid streams through a diverging frusto-conical diffuser passage.
 5. The general regenerative power plant of claim 1 wherein the contact heat exchanger is comprised by an ejector having a centrally-disposed ejector passage surrounded by an outer nozzle passage in the receiving section thereof, and discharges the combined fluid streams through a diverging annular diffuser passage.
 6. Regenerative feed heating means impressed upon the thermo-dynamic processes of a Rankine cycle power plant comprising in combination: a vapor generator having integral heating processes; a heat engine member adapted to expand the cycle working fluid; a vapor-to-liquid condenser member adapted to receive expanded vapor from a discharge outlet of said heat engine member and to condense said expanded vapor to liquid by transfer of heat energy therefrom; an ejector-type fluid-to-fluid contact heat exchanger adapted to effect the regenerative pre-heating of high-velocity feed liquid by contact interchange in parallel flow with expanded heating vapor from a discharge outlet of the said heat engine member; a liquid feed pump; communicating means between the outlet of said vapor generating member and the inlet of said heat engine member for the transfer of heated and pressurized cycle working fluid; communicating means between a discharge outlet of said heat engine member and the inlet of said condenser member for the transfer of expanded cycle working fluid; communicating means between the liquid outlet of said condenser member and the inlet of said feed pump; communicating means between the discharge of said feed pump and accelerating nozzle passageways of said contact heat exchanger; communicating means between a discharge outlet of said heat engine member and ejector passageways of said contact heat exchanger for the transfer of expanded heating vapor; valve regulating means disposed to control flow of the said expanded heating vapor from a discharge outlet of said heat engine member into ejector passageways of said contact heat exchanger to regulate heat absorption by feed liquids passing therethrough; and communicating means between the fluid discharge of said contact heat exchanger and heating processes of said vapor generator member; the said contact heat exchanger being adapted to receive and exchange energy between high-velocity feed liquid and engine-expanded heating vapor in parallel flow within internal fluid passageways thereof, to combine the thermal energy of the several entering fluid streams, and to discharge pressurized and pre-heated feed liquid from diffuser passageways thereof; whereby the external effect of the regenerative feed heating process is to pre-heat cycle feed liquid by contact interchange with engine-expanded heating vapor within said contact heat exchanger, thereby reducing the heat rejection of said power plant and decreasing the quantity of heat energy supplied by said vapor generator member to raise the temperature of the feed liquid to the saturation temperature at the pressure of the evaporation process.
 7. The general regenerative Rankine cycle power plant of claim 6 wherein a plurality of fluid-to-fluid contact heat exchangers are disposed in parallel with respect to each other between common pressurized feed liquid and expanded heating vapor supply headers, and discharges pre-heated feed liquid from said contact heat exchangers to heating processes of said vapor generator member.
 8. The general regenerative Rankine cycle power plant of claim 6 wherein the contact heat exchanger is comprised by an ejector having a centrally-disposed nozzle passage surrounded by an outer ejector passage in the receiving section thereof, and discharges the combined fluid streams through a diverging frusto-conical diffuser passage.
 9. The general regenerative Rankine cycle power plant of claim 6 wherein the contact heat exchanger is comprised by an ejector having a centrally-disposed ejector passage surrounded by an outer nozzle passage in the receiving section thereof, and discharges the combined fluid streams through a diverging annular diffuser passage.
 10. The general regenerative Rankine cycle power plant of claim 6 wherein a plurality of fluid-to-fluid contact heat exchangers having members mounted in parallel with respect to each other is disposed in the liquid feed piping system of said power plant; means for supplying the said plurality of contact heat exchangers with pressurized feed liquid at a common pressure state; means for supplying individual members of the said plurality of contact heat exchangers with expanded heating vapor at different pressure states; and means for transferring the pre-heated feed liquid discharge of said plurality of contact heat exchangers to heating processes of said vapor generator member.
 11. The general regenerative Rankine cycle power plant of claim 6 wherein a plurality of heat engines having members disposed in parallel with respect to each other in the piping system of said power plant is supplied with heated and pressurized cycle working fluid from said vapor generator member; a plurality of fluid-to-fluid contact heat exchangers having members disposed in parallel with respect to each other in the liquid feed piping system of said power plant; means for supplying the said plurality of contact heat exchangers with pressurized feed liquid at a common pressure state; means for supplying some individual members of said plurality of contact heat exchangers with expanded heating vapor from one heat engine member; means for supplying the other individual members of said plurality of contact heat exchangers with expanded heating vapor from the other heat engine members of said power plant; and means for transferring the heated feed liquid discharge of said plurality of contact heat exchangers to heating processes of said vapor generator member.
 12. The general regenerative Rankine cycle power plant process of claim 6 wherein a plurality of fluid-to-fluid contact heat exchangers discharging to an intermediate cycle pressure from a lower cycle pressure having members disposed in parallel with respect to each other in the low-pressure side of the feed piping system of said power plant; means for supplying the said plurality of intermediate-pressure contact heat exchangers with pressurized feed liquid at a common pressure state; means for supplying the said plurality of intermediate-pressure contact heat exchangers with expanded heating vapor at a discrete pressure state from a discharge outlet of said heat engine member; means for transferring the heated feed liquid discharge of said plurality of intermediate-pressure contact heat exchangers to the inlets of a plurality of higher pressure liquid feed pumps; a plurality of high-pressure feed pumps disposed to receive heated intermediate-pressure feed liquid from the discharge of said plurality of intermediate-pressure contact heat exchangers and to discharge the heated feed liquid to a higher cycle pressure; a plurality of fluid-to-fluid contact heat exchangers discharging to the higher cycle pressure having members disposed in parallel with respect to each other in the high-pressure side of the feed piping system of said power plant; means for supplying the said plurality of high-pressure contact heat exchangers with expanded heating vapor at discrete pressure states from discharge outlets of said heat engine member; and means for transferring the heated feed liquid discharge of said plurality of high-pressure contact heat exchangers to heating processes of said vapor generator member.
 13. The general regenerative Rankine cycle power plant process of claim 6 wherein a plurality of regenerative Rankine cycle branches are disposed in parallel with respect to each other and communicate with a common vapor generator member; each individual regenerative Rankine cycle branch having elementary components including the heat engine, vapor-to-liquid condenser, contact heat exchanger, cycle pump, control and communicating means, etc. common to the simple regenerative Rankine cycle of claim 6 excepting the vapor generator member; valve means disposed in the vapor inlet line of each individual cycle branch which may alternately admit pressurized vapor thereinto from the common vapor generator member; and valve means disposed in the feed liquid discharge line of each individual cycle branch which may alternately isolate the said feed liquid discharge line from communication with the common vapor generator member; whereby the common vapor generator and each member of the said plurality of regenerative Rankine cycle branches may be alternately connected to comprise a separate regenerative Rankine cycle power plant.
 14. The general regenerative Rankine cycle power plant process of claim 6 wherein a plurality of vapor generator members are disposed in parallel with respect to each other and communicate with a common regenerative Rankine cycle branch; the common regenerative Rankine cycle branch having elementary components including the heat engine, vapor-to-liquid condenser, contact heat exchanger, cycle pump, control and communicating means, etc. common to the simple regenerative Rankine cycle of claim 6 excepting the vapor generator member; and valve means disposed in the vapor discharge line and feed liquid supply line of each member of the said plurality of vapor generator members; whereby the common regenerative Rankine cycle branch and each member of the said plurality of vapor generator members may be alternately connected to comprise a separate regenerative Rankine cycle power plant.
 15. The general regenerative Rankine cycle power plant of claim 6 wherein a plurality of heat engines having members disposed in parallel with respect to each other in the piping system of said power plant is supplied with heated and pressurized cycle working fluid from a common vapor generator member; one heat engine member of the said plurality being disposed for maximum expansion of its working fluid stream by discharging the major fraction thereof to an adjacent vapor-to-liquid condenser in the low-pressure side of the feed piping system of said power plant, while other limited expansion heat engine members of the said plurality are disposed to discharge their working fluid streams to the high-pressure side of the feed piping system of said power plant; a plurality of fluid-to-fluid contact heat exchangers discharging to an intermediate cycle pressure having members disposed in parallel with respect to each other in the low-pressure side of the feed piping system of said power plant; means for supplying nozzle passageways of the said plurality of intermediate-pressure contact heat exchangers with pressurized feed liquid at a common pressure state; means for supplying the said plurality of intermediate-pressure contact heat exchangers with expanded heating vapor at a discrete pressure state from a discharge outlet of the said maximum expansion heat engine member; means for transferring the heated feed liquid discharge of said plurality of intermediate-pressure contact heat exchangers to the inlet of a liquid feed pump; a high-pressure feed pump disposed to discharge heated intermediate-pressure feed liquid from the said intermediate pressure to a higher cycle pressure; a plurality of fluid-to-fluid contact heat exchangers discharging to the higher cycle pressure having members disposed in parallel with respect to each other in the high-pressure side of the feed piping system of said power plant; means for transferring the pressurized feed discharge of the said high-pressure feed pump to nozzle passageways of the said plurality of high-pressure contact heat exchangers; means for supplying the said plurality of high-pressure contact heat exchangers with expanded heating vapor at discrete pressure states from discharge outlets of the limited expansion heat engine members of the said plurality; and means for transferring the heated feed liquid discharge of the said plurality of high-pressure contact heat exchangers to heating processes of the common vapor generator member.
 16. The general regenerative Rankine cycle power plant of claim 6 wherein a plurality of heat engines having members disposed in parallel with respect to each other in the piping system of said power plant is supplied with heated and pressurized cycle working fluid from a common vapor generator member; one positive-displacement heat engine member of the said plurality being disposed for maximum expansion of its working fluid stream by discharging the major fraction thereof to an adjacent vapor-to-liquid condenser in the low-pressure side of the feed piping system of said power plant, while other non-condensing non-positive displacement heat engine members of the said plurality are disposed for limited expansion of their working fluid streams and discharge to the high-pressure side of the feed piping system of said power plant; a plurality of fluid-to-fluid contact heat exchangers discharging to an intermediate cycle pressure having members disposed in parallel with respect to each other in the low-pressure side of the feed piping system of said power plant; means for supplying nozzle passageways of the said plurality of intermediate-pressure contact heat exchangers with pressurized feed liquid at a common pressure state; means for supplying the said plurality of intermediate-pressure contact heat exchangers with expanded heating vapor at a discrete pressure state from a discharge outlet of the said positive-displacement heat engine member; means for transferring the heated feed liquid discharge of said plurality of intermediate-pressure contact heat exchangers to the inlet of a liquid feed pump; a high-pressure feed pump disposed to discharge heated intermediate-pressure feed liquid from the said intermediate pressure to a higher cycle pressure; a plurality of fluid-to-fluid contact heat exchangers discharging to the higher cycle pressure having members disposed in parallel with respect to each other in the high-pressure side of the feed piping system of said power plant; means for transferring the pressurized feed discharge of the said high-pressure feed pump to nozzle passageways of the said plurality of high-pressure contact heat exchangers; means for supplying the said plurality of high-pressure contact heat exchangers with expanded heating vapor at discrete pressure states from discharge outlets of the limited expansion non-positive displacement heat engine members of the said plurality; and means for transferring the heated feed liquid discharge of the said plurality of high-pressure contact heat exchangers to heating processes of the common generator member. 